TWM481542U - External-rotation type of permanent magnetic brushless electric machine - Google Patents

Description

Externally rotating permanent magnet brushless motor

The utility model relates to an externally rotating permanent magnet brushless motor, in particular to an externally rotating permanent magnet brushless motor with high rigidity transmission and support structure.

The existing belt-driven fitness equipment, such as an exercise bicycle, is a flywheel that the user drives the exercise bicycle by pedaling, and the hybrid brake device causes the flywheel to generate resistance when rotating, thereby allowing the user to step on the exercise bicycle. The heat can be dissipated. Because the braking torque generated by the generator of the hybrid brake device can only provide partial braking force, the main braking force still needs to be additionally provided with a hysteresis braking device. Therefore, please refer to Figures 13 and 14 for the US invention patent. No. 6084325 "Brake device with a combination of power-generating and eddy-current magnetic resistance", which is connected between the two support frames 81 by a drive shaft 82. And a rotor 84 (flywheel) connected to the rotor 84 and one end of which is connected to the exercise equipment, the rotor 84 is disposed on the opposite outer side of the stator 83, and a hysteresis brake device 85 is disposed on the outer side of the rotor 84. The stator 83 is provided with a plurality of sets of coils 831. The rotors 84 are provided with a plurality of permanent magnets 841 in a radial and annular manner, and the two support frames 81 and the stator 83 are opposite to each other. Shaft 82 is provided with a plurality of bearings 811 to When the transmission shaft 82 is rotated by force, the rotor 84 can be rotated together; since the hybrid brake device does not need to consider the power generation braking capability and the electric energy recovery, the kinetic energy generated by the fitness equipment is mostly converted into thermal energy by the hysteresis braking device 85. Loss, can not take into account the quality and efficiency of power generation. Furthermore, as shown in FIG. 14, the brake device is on the torque transmission, and the components on the transmission shaft 82 are fixed to the shaft center, and each component has an axial clearance in the axial arrangement. When the transmission shaft 82 is provided, When rotated by an external force, the axial stress of the transmission shaft 82 cannot be directly and continuously transmitted to the rotor 84, and the two support frames 81 for supporting the rotor 84 and the bearings 811 cannot effectively absorb the torsional force generated by the bearing clearance. The problem of insufficient rigidity of the transmission structure is caused. In addition, most of the locking bolts 86 between the two support frames 81 are lower than the imaginary center line of the transmission shaft 82, and the two support frames 81 are easily caused by the axial force of the transmission shaft 82. The half strength is insufficient to deform, and at the same time, the bearings 811 of the two support frames 81 have a problem of greatly reducing the life due to improper force.

It can be seen from the foregoing that the existing fitness equipment has poor design of the support frame, so that there is a gap between the components and the axial stress cannot be directly and continuously transmitted, resulting in poor rigidity of the overall structure, reduced service life of the parts and energy consumption. The need for improvement.

As mentioned above, the existing fitness equipment has poor design of the support frame, so that there is a gap between the components and the axial stress cannot be directly and continuously transmitted, resulting in poor rigidity of the overall structure, low service life of the parts and energy consumption. The main problem of the present invention is to provide an externally-rotating permanent magnet brushless motor, mainly in which the components on the transmission shaft are adjacent to each other without an axial gap transmission structure, and are axially preloaded. The mechanism reduces the bearing gap and improves the rigidity of the transmission structure. The joint between the other two support frames is distributed around the support frame and one or more of the joint members are above the center point of the transmission shaft, which can reduce the deformation of the support frame. Improve the life of parts and solve the problems of poor structural rigidity, low service life and energy consumption of existing fitness equipment.

The main technical means adopted for achieving the foregoing purpose is that the externally-rotating permanent magnet brushless motor mainly has a flywheel, a stator and a rotor between a front support frame and a rear support frame, and the flywheel has a first surface. And a second surface, the first surface of which is closed, and the second surface is concavely formed for fixing the rotor, the rotor ring is disposed on the outer side of the stator and is rotatable relative to the stator, wherein the front and rear supports The front frame is provided with a front bearing seat and a rear bearing seat. One end of the front bearing seat is connected with the front support frame, and is provided with a front bearing and one or more front washers. The front bearing and the front washer are clamped in front. Between the bearing seat and the first side of the flywheel, one end of the rear bearing seat is connected to the stator and the other end is connected to the rear bracket, and a wave spring is arranged between the rear bearing seat and the second surface of the flywheel. a rear bearing and more than one rear washer, the front and rear bearings are penetrated by a transmission shaft, and the transmission shaft is connected with the flywheel to rotate the rotor relative to the stator, and the front and rear support frames are provided at the periphery The plurality of coupling members are coupled to each other, and one or more of the coupling members are located above a center point of the transmission shaft.

The externally rotating permanent magnet brushless motor composed of the foregoing components is provided with a flywheel, a rotor and a stator between the front and rear bearing seats on the front and rear support frames, and the flywheel is driven by the drive shaft to rotate the rotor around the stator. When the shaft is pulled by the lateral force, since the components on the transmission shaft are adjacent to each other without the axial clearance transmission structure, and the axial preloading mechanism reduces the bearing clearance, the elastic deformation of the front and rear support frames is not easily generated. The bearing of the front and rear bearing housings can be prevented from being improperly stressed and the rigidity is greatly increased. The other coupling members are distributed around the support frame, and one or more of the coupling members are located above the center point of the transmission shaft to strengthen the rigidity of the supporting mechanical structure. The problem of reducing the deformation of the support frame can improve the life of the parts, and solve the problem that the existing fitness equipment has poor structural rigidity, low service life of components and energy consumption.

10‧‧‧ Stator

11‧‧‧矽Steel sheet

12‧‧‧ wire trough

13‧‧‧ coil

21‧‧‧Rotor

211‧‧‧through slot

22‧‧‧ permanent magnet

23‧‧‧Flywheel

231‧‧‧Axis hole

24‧‧‧ drive shaft

241‧‧‧Double round key

25‧‧‧ bolt

26‧‧‧ Pulley

31‧‧‧ front bearing housing

311‧‧‧ front bearing hole

312‧‧‧ front bearing

313‧‧‧C buckle

314‧‧‧ front washer

315‧‧‧ screws

32‧‧‧ rear bearing housing

321‧‧‧ rear bearing hole

322‧‧‧ rear bearing

323‧‧‧ Wave spring

324‧‧‧After washer

325‧‧‧ screws

326‧‧‧Bolts

41‧‧‧ Front support

411‧‧‧ front through hole

412‧‧‧Lock hole

42‧‧‧After support

421‧‧‧After through hole

422‧‧‧Lock hole

43‧‧‧Lock bolts

431‧‧‧ nuts

51‧‧‧Sensor board

511‧‧‧ sensor

81‧‧‧Support frame

811‧‧‧ bearing

82‧‧‧ drive shaft

83‧‧‧ Stator

831‧‧‧ coil

84‧‧‧Rotor

841‧‧‧ permanent magnet

85‧‧‧Magnetic brake device

86‧‧‧Lock bolts

1 is a perspective view of a preferred embodiment of the present invention.

Figure 2 is an exploded view of the preferred embodiment of the present invention.

Figure 3 is a partial cross-sectional view of the preferred embodiment of the present invention.

Figure 4 is a side elevational view of the preferred embodiment of the present invention.

Figure 5 is a side elevational view of the rotor of the preferred embodiment of the present invention.

Figure 6 is a schematic illustration of a three-section arc of the preferred embodiment of the present invention.

Figure 7 is a schematic diagram showing the comparison of total harmonic distortion of the preferred embodiment of the present invention.

FIG. 8 is a schematic diagram showing the comparison of the torsion torque standard of the preferred embodiment of the present invention. .

Figure 9 is a schematic illustration of the comparison of the resonant frequency and the amount of vibration of the preferred embodiment of the present invention.

FIG. 10 is a schematic diagram showing the configuration of a sensor of the preferred embodiment of the present invention.

Figure 11 is a side elevational view of another aspect of the support frame of the preferred embodiment of the present invention.

Figure 12 is a side elevational view of a further embodiment of the support frame of the preferred embodiment of the present invention.

Fig. 13 is an external view of a conventional brake device.

Figure 14 is a cross-sectional view showing a conventional brake device.

With respect to a preferred embodiment of the present invention, as shown in Figures 1 to 3, a rotatable rotor 21 is provided on the outer ring of the periphery of the stator 10, and a plurality of permanent magnets 22 are disposed in the rotor 21 and are disposed on the rotor. A flywheel 23 is fixed on the outer side of the periphery of the 21, and a front support frame 41 and a rear support frame 42 are respectively disposed on opposite sides of the stator 10. The stator 10 is connected to the rear support frame 42. The front support frame A rear bearing housing 31 is disposed at one end of the flywheel 23, and a rear bearing housing 32 is disposed at one end of the rear bearing bracket 42. A transmission shaft 24 is disposed between the front bearing housing 31 and the rear bearing housing 32. And the transmission shaft 24 is connected to the flywheel 23.

The stator 10 is mainly formed by stacking a plurality of circular steel sheets 11 each having a plurality of radially-shaped wire grooves 12 formed at the periphery thereof, and the wire grooves 12 are provided for winding multiple groups. The coil 13 and the surface of each of the silicon steel sheets 11 are coated with an insulating layer, and an insulating sheet (not shown) is interposed between the outermost silicon steel sheet 11 and the coil 13; in the preferred embodiment, The The winding manner of the coil 13 is not limited.

The flywheel 23 has a first surface and a second surface, the first surface of which is closed, and the second surface is concavely formed for receiving and fixing the rotor 21. The rotor 21 is annular. Surrounding the outer side of the stator 10 and rotating relative to the stator 10, the rotor 21 is formed with a plurality of slots 211 which are axially penetrated through the front and rear side walls thereof and are annularly arranged with the outer shape of the rotor 21, and the through slots 211 It is a square shape for accommodating a plurality of pairs of permanent magnets 22, and each pair of permanent magnets 22 has a square shape; as shown in FIG. 2, the rotor 21 is formed with a plurality of keyholes for locking the flywheel through a plurality of bolts 25. 23, the flywheel 23 is formed at the center of the first surface thereof with a shaft hole 231, wherein the shaft hole 231 is for the transmission shaft 24 to pass through, and the transmission shaft 24 and the shaft hole 231 of the flywheel 23 respectively form a groove. For a pair of round key 241 to be inserted and fixed. Further, the transmission shaft 24 is provided with a pulley 26 at the opposite end of the front bearing housing 31. The transmission shaft 24 and the pulley 26 are respectively formed with grooves for inserting and fixing another double-headed round key 241, and the pulley 26 is provided for external devices. A rotational force is input (such as a fitness equipment) to drive the flywheel 23 and the rotor 20 to rotate relative to the stator 10.

A front bearing hole 311 is formed in the center of the front bearing housing 31. The front bearing hole 311 is provided with a front bearing 312. The front bearing 312 is sleeved at one end of the transmission shaft 24 and is coupled to the front bearing 312 and the flywheel 23. Further disposed between the first face is a C-shaped buckle 313 and a front washer 314 which abuts against the inner edge of the front bearing hole 311 to prevent unintended axial displacement of the front bearing 312. The front washer 314 is clamped to the front bearing 312 and The flywheels 23 are filled between the flywheels 23, and the front bearing housing 31 is locked to the front support frame 41 by a plurality of screws 315.

A rear bearing hole 321 is formed in the center of the rear bearing housing 32. The rear bearing hole 321 is provided with a rear bearing 322, and a wave spring 323 is interposed between the rear bearing hole 321 and the rear bearing 322. The rear bearing 322 is attached. The sleeve is disposed on the other end of the transmission shaft 24 with respect to the front bearing 312, and a rear washer 324 is interposed between the rear bearing 322 and the second surface of the flywheel 23, and the rear washer 324 is used to fill the axial gap. The rear bearing housing 32 is locked to the rear support frame 42 by a plurality of screws 325, and the stator 11 is locked to the rear bearing housing 32 via a plurality of bolts 326.

In the preferred embodiment, the front support frame 41 is in the shape of a sheet and has a T-shape. The front support frame 41 is formed with a front through hole 411 at the center of the T-shaped top end. The rear support frame 42 is also formed. The front support frame 42 is formed in a T-shape, and the rear support frame 42 is formed with a rear through hole 421 corresponding to the front support frame 41. The front support frame 41 and the rear support frame 42 respectively form a majority. The locking holes 412 and 422 are coaxially disposed for the plurality of locking bolts 43 and are coupled to each other at both ends of the locking bolt 43 by a nut 431 so that the front support frame 41 and the rear support frame 42 are equiaxed relative to each other. As shown in FIG. 4 , the front support frame 41 and the rear support frame 42 are respectively formed with four locking holes 412 and 422 on the two sides of the T-shaped proximal end, and four locking bolts 43 are disposed. The nut 431 has two locking bolts 43 and a nut 431 thereof above the center point A of the transmission shaft 24 or the pulley 26, and at least two The locking bolts 43 and the corresponding nuts 431 are located below the center point A of the transmission shaft 24 or the pulley 26, whereby the locking holes 412 are respectively disposed at the corners of the front support frame 41 and the rear support frame 42, After the 422 and the locking bolt 43 and the nut 431 are combined with each other, the overall structural strength of the front support frame 41 and the rear support frame 42 can be strengthened, and the mechanical rigidity of the front support frame 41 and the rear support frame 42 can be increased. The elastic deformation of the front support frame 41 and the rear support frame 42 is easily generated, and the front bearing 32 and the rear bearing 36 are prevented from being subjected to an improper lateral force, and the problems of the front and rear support frames 41, 42 being deformed by force are reduced.

The front washer 314 and the rear washer 324 are geometrically configured to fill different axial dimension gaps between the flywheel 23 and the front bearing 312 and the rear bearing 322, respectively, simplifying the structure of the drive shaft 24 and improving the commonality, thereby reducing manufacturing. The purpose of the process and cost. The pulley 26 is for inputting a rotational force by an external device (such as a fitness equipment) to drive the flywheel 23 and the rotor 21 to rotate through the transmission shaft 24, the pulley 26, the front bearing 312, the front washer 314, the flywheel 23, the rear washer 324 and the rear bearing 321 is a non-axial gap transmission structure adjacent to each other, which is beneficial to the continuous transmission of the structural stress of the torque and the side tension of the pulley 26, and the wave spring 323 built in between the rear bearing 322 and the rear bearing housing 32 as the front bearing. The preloading mechanism of 312 and rear bearing 322 strengthens the rigidity of its bearing set.

As can be seen from the above, the technical features of the present invention are:

1. The stator 10 is coupled to the rear bearing housing 32, and the rear bearing housing 32 has a built-in Wave spring 323.

2. The rotor 21 is coupled to the flywheel 23, the flywheel 23 is coupled to the drive shaft 24, and the second surface of the flywheel 23 is sequentially adjacent to the rear washer 324 and the rear bearing 322, and the rear bearing 322 is axially locked and coupled to the rear bearing housing 32. Combine.

3. The front bearing 312 is coupled to the front bearing housing 31, and the first face of the flywheel 23 is sequentially adjacent to the front washer 314 and the front bearing 312, and the pulley 26 is axially locked.

4. The front bearing block 31 is coupled to the front support frame 41, the rear bearing block 32 is coupled to the rear support frame 42, and the front support frame 41 and the rear support frame 42 are locked by a plurality of locking bolts 43 and a plurality of nuts 431 .

5. The front support frame 41 and the rear support frame 42 have more than one locking hole 412, 422 around the rear support frame 42 and are provided with a locking bolt 43 and a corresponding nut 431, the locking hole 412, 422, the locking bolt 43 and nut 431 are higher than the center point of the drive shaft 24.

It can be seen from the above that the components provided on the transmission shaft 24 are non-axial clearance transmission structures adjacent to each other, and the bearing clearance is reduced by the axial preloading mechanism, and the front support frame 41 and the rear support frame 42 are not easily generated. The elastic deformation can avoid the improper bearing of the bearings of the front and rear bearing seats 31, 32 and greatly improve the structural rigidity, and the other locking bolts 43 are distributed around the front support frame 41 and the rear support frame 42, and more than one The locking bolt 43 is higher than the center point of the transmission shaft 24, which can reduce the doubts of the deformation of the upper half of the front support frame 41 and the rear support frame 42, thereby improving the life of the component and solving the existing fitness equipment. Poor structural rigidity, low component life and energy loss.

Referring to FIGS. 5 and 6, the ratio of the number of slots of the slot 10 of the stator 10 to the number of poles of the rotor 21 is an integer ratio of 6 or 6, that is, the width range of each pair of permanent magnets 22 corresponds to 6 slots 12, the ratio may also be 12, 18 or 24; since each pole of the rotor 21 is composed of one or a pair of permanent magnets 22, each pole corresponds to the outer circumference of the rotor 21 of the 6 slots 12. It is a three-stage arc edge, and includes a first arc edge A1, a second arc edge A2 and a third arc edge A3. The following describes the design of each arc edge.

As shown in FIG. 5, five reference lines are formed between the ends of each of the magnetic poles, which are respectively a first reference line to a fifth reference line (L1 to L5), and the reference lines are rotors. The center point CR of 21 is outwardly radial as a reference, wherein the first reference line L1 is the tenth reference point P10 of the center point CR of the rotor 21 passing through the center of the tooth comb of the stator 10 and the first arc side A1 An outwardly extending line of reference point P1, and the rotor 21 is considered to be facing the stator 10. The second reference line L2 is an outward extension of the center point CR of the rotor 21 from the first reference line L1 by an outer distance D of the stator 10. The third reference line L3 is the center point CR of the rotor 21 and is equally spaced from the first reference line L1 by an outward extension of the pitch 10 of the stator 10, but the third reference line L3 and the second reference line L2 are different sides. . The fourth reference line L4 is an outward extension line of the center point CR of the rotor 21, the eighth reference point P8 of the stator 10, and the sixth reference point P6 of the corner of one of the permanent magnets 22. The The fifth reference line L5 is an outward extension line of the center point CR of the rotor 21, the ninth reference point P9 of the stator 10, and the seventh reference point P7 of the corner of the other permanent magnet 22. That is, the angle at which the center point CR of the rotor 21 is developed with respect to the three-stage arc side of the outer circumference of the permanent magnet 22 and the rotor 21 is within the range of the angle between the fourth reference line L4 and the fifth reference line L5.

The distance between the center point CR of the rotor 21 and the first reference point P1 of the first arc side A1 is R1, and the distance between the center C1 of the first reference circle S1 and the first reference point P1 of the first arc side A1 is R2, and fourth. The distance from the center C0 of the reference circle S4 to the center point CR of the rotor 21 is R3; the radius of the fourth reference circle S4 is equal to R1+R2+R3. Wherein (R1+R2)/R3≒0.56-0.68.

The intersection of the first reference line L1 and the fourth reference circle S4 is the center C1 of the first reference circle S1, the intersection of the second reference line L2 and the fourth reference circle S4 is the center C2 of the second reference circle S2, and the third reference line L3 is The intersection of the fourth reference circle S4 is the center C3 of the third reference circle S3, and the first reference circle S1, the second reference circle S2 and the third reference circle S3 have the same radius R2.

The circumferential intersection of the circumference of the first reference circle S1 and the second reference circle S2 is the adjacent second reference point P2 of the first arc side A1 and the second arc side A2, the circumference of the first reference circle S1 and the third reference circle S3 The circumferential intersection point is the adjacent third reference point P3 of the first arc side A1 and the third arc side A3. The intersection of the circumference of the second reference circle S2 and the fourth reference line L4 is the fourth reference point P4 of the second arc side A2, and the intersection of the circumference of the third reference circle S3 and the fifth reference line L5 is The fifth reference point P5 of the third arc side A3.

Referring to FIG. 7, the top of FIG. 7 is that the rotor 21 is not provided with a three-stage arc, and the bottom of FIG. 7 is provided with a three-stage arc for the rotor 21. As can be seen from FIG. 7, the coil 13 of the stator 10 generates an induced potential. The total harmonic distortion percentage (Mag) analysis can be suppressed to 6.4%, which can reduce the total harmonic distortion by 67% compared with the unused three-section arc edge, and improve the power quality of power generation by effectively suppressing the percentage of total harmonic distortion. With efficiency.

Please refer to Figure 8, using the above three-stage arc edge design (solid line as shown), the value of the torque can be suppressed to 0.39, compared to the unused three-section arc design (such as The dotted line shown in the figure can be reduced by 61%, and reducing the torque can directly improve the comfort of use.

Referring to FIG. 9 , the front support frame 41 is subjected to vibration measurement near the front bearing 32. The upper part of FIG. 9 is not implemented before, and the lower part of FIG. 9 is implemented, the main natural resonance frequency can be increased from 46 Hz before the implementation. 68 Hz after implementation, improved by more than 48%; if the vibration is compared at a natural resonance frequency of 46 Hz, the vibration amount can be suppressed to 0.01 g/N or less, and the improvement is over 67%, which can be greatly improved. The life of the rigid drive and support structure.

As shown in FIG. 2 and FIG. 10, the rear support frame 42 is provided with a sensing circuit board 51. The sensing circuit board 51 is provided with three sensors 511, and the sensors 511 are correspondingly disposed on the sidewall of the rotor 21. Each pair of permanent magnets 22 detects the change in magnetic force. Since each pair of permanent magnets 22 is in the rotor 21 The concentric circles of the heart points are approximately distributed to form a first reference tangent T1 and a second reference tangent T2, wherein the first reference tangent T1 is inscribed in each pair of permanent magnets 22, and the second reference tangent T2 is exogenous to Each pair of permanent magnets 22, the sensors 511 are at an appropriate axial distance from each pair of permanent magnets 22, and are distributed over the first reference tangent T1 or the second reference tangent T2.

Thereby, the sensors 511 can sense the axial leakage flux of each pair of permanent magnets 22 of the rotor 21 and provide reference position sensing information of the magnetic poles of the rotor 20 to serve as a future without significantly increasing product cost. The parameter basis for high-efficiency power generation and mains parallel recovery control.

With respect to another embodiment of the support frame 41 and the rear support frame 42 of the preferred embodiment of the present invention, referring to FIG. 11, the front support frame 41 is in the form of a sheet and has a slightly inverted L shape. The rear support frame 42 is also in the form of a sheet and has a slightly inverted L shape. One of the locking bolts 43 and the nuts 431 are disposed above the center point A of the transmission shaft 24, and as shown in FIG. 12, the front support is provided. Two of the locking bolts 43 of the frame 41 and the rear support frame 42 and the nuts 431 are disposed above the center point A of the transmission shaft 24.

It can be seen from the above that the components on the transmission shaft 24 are adjacent to each other without the axial clearance transmission structure on the shaft center, and the axial preloading mechanism reduces the gap between the bearings to improve the rigidity of the transmission structure. The other locking bolts 43 are distributed around the front and rear support frames 41 and 42 to reduce the deformation of the front and rear support frames 41 and 42 to improve the life of the components, and to solve the problem that the existing fitness equipment has poor structural rigidity and low service life of the components. With the problem of energy loss.

10‧‧‧ Stator

11‧‧‧矽Steel sheet

12‧‧‧ wire trough

13‧‧‧ coil

21‧‧‧Rotor

211‧‧‧through slot

22‧‧‧ permanent magnet

23‧‧‧Flywheel

231‧‧‧Axis hole

24‧‧‧ drive shaft

241‧‧‧Double round key

25‧‧‧ bolt

26‧‧‧ Pulley

31‧‧‧ front bearing housing

311‧‧‧ front bearing hole

312‧‧‧ front bearing

313‧‧‧C buckle

314‧‧‧ front washer

315‧‧‧ screws

32‧‧‧ rear bearing housing

321‧‧‧ rear bearing hole

322‧‧‧ rear bearing

323‧‧‧ Wave spring

324‧‧‧After washer

325‧‧‧ screws

326‧‧‧Bolts

41‧‧‧ Front support

411‧‧‧ front through hole

412‧‧‧Lock hole

42‧‧‧After support

421‧‧‧After through hole

422‧‧‧Lock hole

43‧‧‧Lock bolts

431‧‧‧ nuts

51‧‧‧Sensor board

511‧‧‧ sensor

Claims (15)

An externally rotating permanent magnet brushless motor mainly comprises a flywheel, a stator and a rotor between a front support frame and a rear support frame, the flywheel having a first side and a second side, the first side of the flywheel The second surface is formed in a concave shape for fixing the rotor. The rotor ring is disposed on the outer side of the stator and rotatable relative to the stator. The front and rear support frames are respectively provided with a front bearing seat and a front bearing seat. a rear bearing seat, one end of the front bearing seat is connected to the front support frame, and is provided with a front bearing and one or more front washers, the front bearing and the front washer are sandwiched between the front bearing seat and the first side of the flywheel One end of the rear bearing seat is connected to the stator and the other end is connected to the rear bracket, and a wave spring, a rear bearing and one or more rear washers are interposed between the rear bearing seat and the second surface of the flywheel. The front and rear bearings are inserted through a transmission shaft, and the transmission shaft is connected with the flywheel to rotate the rotor relative to the stator, and the front and rear support frames are provided with a plurality of coupling members at the periphery to be combined with each other, and one or more of the couplings are combined The piece is located in the drive shaft Above the point. A rotary permanent magnet brushless motor as claimed in claim 1, wherein the rotor is provided with a plurality of permanent magnets, and the rotors corresponding to the magnetic pole ranges of the permanent magnets are formed with three-stage arc edges. The external permanent magnet brushless motor according to claim 2, wherein the flywheel has a shaft hole formed at a center of the first surface, the shaft hole is for the transmission shaft to be inserted therein, and the shaft hole of the transmission shaft and the flywheel are respectively A groove is formed, and the two grooves are commonly inserted into a double round key. The outer permanent magnet brushless motor according to claim 3, wherein the front bearing housing of the front support frame is formed with a front bearing hole, and the bearing hole receives the front bearing and A C-shaped buckle abuts against the inner edge of the front bearing bore. The outer permanent magnet brushless motor according to claim 4, wherein the rear bearing housing of the rear support frame is formed with a rear bearing hole, the rear bearing hole receiving the rear bearing, and the rear bearing and the rear bearing hole There is a wave spring between them. The external permanent magnet brushless motor according to claim 5, wherein the transmission shaft is provided with a pulley at the other end of the opposite flywheel of the front support frame, and the transmission shaft and the pulley respectively form a groove, and the two grooves are common Plug in another double round key. The external permanent magnet brushless motor according to claim 6, wherein the front and rear support frames respectively form a plurality of locking holes around the fastening members, and the coupling members are locking bolts, and the locking holes and the locking bolts are oppositely fixed. Co-threaded and combined with more than one nut. The external permanent magnet brushless motor according to claim 7, wherein the rear support frame is provided with a sensing circuit board, and the sensing circuit board is provided with more than one sensor, and the sensor is corresponding to each side of the rotor side wall. permanent magnet. The external permanent magnet brushless motor according to claim 8, wherein the permanent magnets are approximately distributed by concentric circles of the center points of the rotors, and the edges of the permanent magnets form an imaginary first reference tangent T1 and a second reference. Tangent T2, the first reference tangent T1 is inscribed in each pair of permanent magnets, and the second reference tangent T2 is externally cut to each pair of permanent magnets, the sensors being at an appropriate axial distance from each pair of permanent magnets, and It is distributed on the first reference tangent T1 or the second reference tangent T2. The external permanent magnet brushless motor according to any one of claims 1 to 9, wherein the front and rear support frames are in the form of a sheet and have an inverted L shape, wherein the locking hole of one of the coupling members is Located above the center point of the drive shaft. The outer-rotating permanent magnet brushless motor according to any one of claims 1 to 9, wherein the front and rear support frames are in a sheet shape and have a T-shape in appearance, and are respectively disposed at two ends of the T-shape. There is a coupling member, and the locking holes of the two coupling members are located above the center point of the transmission shaft. The outer-rotating permanent magnet brushless motor according to any one of claims 2 to 9, wherein the stator is formed by laminating a plurality of circularly-shaped silicon steel sheets, and each of the silicon steel sheets is formed with a plurality of radiations at a periphery thereof. The linear groove has a ratio of the number of slots of the slot to the number of poles of the permanent magnet of the rotor as an integer ratio of six. According to the external permanent magnet brushless motor of claim 12, five reference lines are formed in the range of the rotor corresponding to the magnetic pole range of each permanent magnet, and the first reference line L1 is the center point CR of the rotor passing through the stator. An outwardly extending line of the tenth reference point P10 of the center of the tooth comb and the first reference point P1 of the first arc side A1. An external permanent magnet brushless motor as claimed in claim 13 , wherein the second reference line L2 is an outward extension line of the stator pitch R of the center point CR of the rotor and the first reference line L1; The reference line L3 is the center point CR of the rotor and is equally spaced from the first reference line L1 by an outwardly extending line of the stator pitch D, but on the different side from the second reference line L2. The external permanent magnet brushless motor according to claim 14, wherein the fourth reference line L4 is a center point CR of the rotor, an eighth reference point P8 of the stator, and a sixth reference point P6 of a permanent magnet corner thereof. An outward extension line; the fifth reference line L5 is an outward extension line of a center point CR of the rotor, a ninth reference point P9 of the stator, and a seventh reference point P7 of another permanent magnet corner, the fourth reference The position between the line L4 and the fifth reference line L5 is a three-stage arc edge.